US9341114B2 - Gas power plant - Google Patents

Gas power plant Download PDF

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Publication number
US9341114B2
US9341114B2 US14/379,439 US201314379439A US9341114B2 US 9341114 B2 US9341114 B2 US 9341114B2 US 201314379439 A US201314379439 A US 201314379439A US 9341114 B2 US9341114 B2 US 9341114B2
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Prior art keywords
heat exchanger
generator
gas
fluid
motor
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Expired - Fee Related
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US14/379,439
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US20150035277A1 (en
Inventor
Christian Brunhuber
Oliver Hirschfelder
Uwe Lenk
Wolfgang Menapace
Nicolas Vortmeyer
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Siemens Energy Global GmbH and Co KG
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Siemens AG
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Assigned to SIEMENS AKTIENGESELLSCHAFT reassignment SIEMENS AKTIENGESELLSCHAFT ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: HIRSCHFELDER, Oliver, VORTMEYER, NICOLAS, BRUNHUBER, CHRISTIAN, LENK, UWE, MENAPACE, WOLFGANG
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Assigned to Siemens Energy Global GmbH & Co. KG reassignment Siemens Energy Global GmbH & Co. KG ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: SIEMENS AKTIENGESELLSCHAFT
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use
    • F02C6/18—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use using the waste heat of gas-turbine plants outside the plants themselves, e.g. gas-turbine power heat plants
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use
    • F02C6/04—Gas-turbine plants providing heated or pressurised working fluid for other apparatus, e.g. without mechanical power output
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use
    • F02C6/14—Gas-turbine plants having means for storing energy, e.g. for meeting peak loads
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/18—Structural association of electric generators with mechanical driving motors, e.g. with turbines
    • H02K7/1807—Rotary generators
    • H02K7/1823—Rotary generators structurally associated with turbines or similar engines
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E20/00—Combustion technologies with mitigation potential
    • Y02E20/14—Combined heat and power generation [CHP]

Definitions

  • the present invention relates to a method for operating a gas power plant, comprising a gas turbine which is connected to a generator via a shaft, wherein the generator is designed to be also operated as a motor. Furthermore, the invention relates to such a gas power plant.
  • the temporary storage of electric energy in the form of mechanical energy is especially suitable for short-term or medium-term energy storage.
  • the quantities of surplus electric energy which are available in the public electricity supply network are typically used for altering the storage medium with regard to its mechanical energy state.
  • water for example, is raised to a higher potential energy level by means of suitable pumping devices in order to drive turbines and generators for power generation in a time-staggered manner by means of the water falling to its original level.
  • the current can be fed again into the public electricity supply network and above all can be made available for times at which there is an increased demand for power or regulation.
  • a disadvantage of the conventional storage power plant technologies is their local limitation with regard to their possible application. Therefore, pump storage power plants in most cases can only be used where the local topography features suitable height differences, for instance. In addition to these disadvantages, an undesirable invasion into the appearance of the landscape and into nature is also frequently cause for complaint. Above all, as a result of the necessary erection of large constructional devices above ground such disadvantages can hardly be avoided.
  • this object is achieved by a method for operating a gas power plant comprising a gas turbine, which has a compressor stage and a turbine stage, and is connected to a generator via a shaft, wherein the generator is designed to be also operated as a motor, which method comprises the following steps: —operating the generator as a motor for the rotational operation of the shaft; —simultaneous diverting of the gas flow which discharges from the turbine stage and —feeding this gas flow to a first heat exchanger for transferring thermal energy from the gas flow to a heat exchanger fluid; —feeding the heat exchanger fluid to a thermal store.
  • this object is achieved by a method for operating a gas power plant comprising a gas turbine, which has a compressor stage and a turbine stage, and is connected to a generator via a shaft, wherein the generator is designed to be also operated as a motor, which method comprises the following steps: —operating the generator as a motor for the rotational operation of the shaft; —simultaneous diverting of the gas flow which discharges from the turbine stage and —feeding this gas flow to a first heat exchanger for transferring thermal energy from the gas flow to a heat exchanger fluid; —transferring thermal energy of the heat exchanger fluid to a thermal storage fluid, which thermal storage fluid is fed to a thermal store in a further step.
  • a gas power plant comprising a gas turbine, which has a compressor stage and a turbine stage, and is connected to a generator via a shaft, wherein the generator is designed to be also operated as a motor, furthermore comprising a gas routing device which interacts with the turbine stage in such a way that a gas flow, which discharges from the turbine stage, is diverted and fed to a first heat exchanger, wherein the heat exchanger is designed to extract thermal energy from the gas flow and to transfer it to a heat exchanger fluid which can be introduced in a thermal store for temporary storage.
  • a gas power plant comprising a gas turbine, which has a compressor stage and a turbine stage, and is connected to a generator via a shaft, wherein the generator is designed to be also operated as a motor, furthermore comprising a gas routing device which interacts with the turbine stage in such a way that a gas flow, which discharges from the turbine stage, is diverted and fed to a first heat exchanger, wherein the heat exchanger is designed to extract thermal energy from the gas flow and to transfer it to a heat exchanger fluid which in a second heat exchanger can release at least some of the thermal energy to a heat storage fluid which can be introduced in a thermal store for temporary storage.
  • the conversion of electric energy into thermal energy is therefore carried out.
  • This conversion can be achieved by means of gas power plant technology which already exists at a large number of sites specifically by the generator, which is provided for electric power generation, being adapted to the extent that it can also be operated as a motor for generating a thermally heated gas flow.
  • the use of electric energy which can be drawn from the public electricity supply network, is carried out for the rotational operation of the shaft.
  • This drives the turbine stage and compressor stage which are covered by the gas turbine and therefore ensure a gas flow through the gas turbine which corresponds to the flow during a power generating operation of the gas turbine.
  • no power generation is to be carried out in the case of the operation according to the invention, but only the conversion of electric energy into a suitable, storable form of energy. Power is therefore consumed.
  • the power consumption on account of the large inertia of shaft, compressor and turbine of the gas turbine, acts in a frequency stabilizing manner upon the network frequency of the public supply network.
  • the generator for generating thermal energy by means of the gas turbine air is first of all drawn into the compressor stage from the environment in order to compress this air and therefore to achieve at least partially an adiabatic heating of this thereby compressed air. Consequently, during operation, according to the invention, of the generator as a motor relatively hotter air discharges from the compressor stage and passes through the combustion chamber stage and also the turbine stage. Discharging from the turbine stage, the gas can be diverted in a suitable manner, wherein its thermal energy, after suitable guiding, can be transferred to a heat exchanger fluid by means of thermal interaction in a first heat exchanger.
  • This heat exchanger fluid can be stored in a thermal store for further use at a later time, such as for re-conversion in the event of higher power demands in the public electricity supply network.
  • the gas power plant can also be designed so that the heat exchanger fluid can transfer its thermal energy in a second heat exchanger to a thermal store fluid which is then also stored in a thermal store.
  • the thermal energy of the heat exchanger fluid and/or of the thermal store fluid are, or is, also available for further thermal applications at a later point in time. Such applications are especially advantageously carried out at times at which power from the public electricity supply networks is relatively expensive.
  • thermal store is a component which is not covered by an already existing steam generator unit which is provided for steam generation for the operation of a steam turbine.
  • the thermal store is rather an additional component which is not covered by a conventional gas and steam power plant.
  • gas power plant is to be understood in a broad sense.
  • a combined gas and steam power plant in which a steam turbine is driven by means of the thermal waste heat of the flue gas of a gas turbine, is also to be understood by a gas power plant.
  • a gas power plant which supplies an external steam power plant with thermal heat is also covered by this.
  • a large-scale process-engineering application which has a gas turbine for power generation, is to be understood by a gas power plant.
  • the generator is operated as a motor at variable rotational speed.
  • Such an operation allows different quantities of electric energy to be drawn from the electricity supply network and can therefore be adapted in a suitable manner to the quantity of available surplus power.
  • a variable operation also allows the provision of a gas flow of different temperatures as a result of different compression outputs. According to corresponding temperature selection, the gas flow can subsequently be adapted with regard to its heat content to the requirements of the application.
  • the generator can be operated as a motor in such a way that the gas flow has at least a temperature of 100° C., preferably of at least 150° C. and most especially preferably of at least 300° C.
  • the motor output or the rotational speed is to be adapted to correspond to the temperature of the gas flow. Since in the case of a higher compressor mass flow, and therefore higher compressor exit pressure, an enhanced compression rate of the motor also results, higher quantities of heat at higher temperatures can sometimes be transferred to the gas flow in the event of such operating conditions. This advantageously makes itself particularly advantageously felt in the case of temperature-controlled methods for producing thermal energy, or temperature-controlled steps of such methods. If during compression without additional firing in the gas turbine a temperature level of between 120° C. and 200° C. is to be expected, then with suitable additional firing a higher temperature level of more than 200° C., especially even of more than 300° C., can also be achieved.
  • the generator as a motor for releasing thermal energy by means of the gas flow
  • fuel is fed to the gas turbine in a quantity which is less than a quantity which is fed to the gas turbine during normal power-generating operation, wherein the fuel is combusted in the gas turbine for generating thermal energy.
  • the compression rate in the compressor stage should not be sufficient in order to achieve a predetermined temperature level of the gas flow
  • fuel can be fed to this in the gas turbine and is then combusted by ignition. The combustion serves for the provision of thermal energy which is transferred to the gas flow.
  • the supplying of the gas flow with fuel differs, however, according to the embodiment from a normal operation of the gas turbine for power generation to the effect that the thermal energy is not provided for operation of the turbine stage in the gas turbine to the same extent as in the case of a conventional operation.
  • the thermal energy serves on the one hand for increasing the thermal energy content of the gas flow to a level which does not normally enable the normal operation of the turbine stage.
  • the additional firing of fuel, for example natural gas, in the combustion chamber also enables a release of thermal power in the turbine stage, as a result of which a mechanical drive of this is achieved which, however, is lower than in the case of a normal operation.
  • the motor can be unloaded and even controlled with regard to power consumption.
  • smaller quantities of fuel are required than in comparison to a conventional operation for power generation.
  • the temperature or the thermal energy content of the gas flow can therefore be advantageously increased.
  • the operation of the generator as a motor for releasing thermal energy by means of the gas flow follows the operation of the generator in a normal power generating operation of the generator with a time delay of less than one hour, preferably of less than half an hour.
  • normal operation is be understood by full-load operation.
  • relatively short changes between full load during power generation and an operation for drawing current from the electricity supply networks, with simultaneous storage of generated thermal heat can also be achieved.
  • the specified bridging times serve typically for thermal equalization during ramping down of the gas turbine for power generation. Such bridging times are necessary so that there is especially no need to fear thermal damage to the gas power plant as a result of an excessively rapid load changed from, for example, full load to a power consuming operation.
  • the extraction of the heat exchanger fluid and/or of the thermal store fluid from the thermal store is carried out, wherein the extracted heat exchanger fluid and/or the thermal store fluid is fed to a steam application as process steam or for the preparation of process steam.
  • a steam application can preferably be the supply of industrial processes with steam from a water-steam cycle, into which the process steam is introduced.
  • the extraction of the heat exchanger fluid and/or of the thermal store fluid from the thermal store is carried out, wherein the extracted heat exchanger fluid and/or the thermal store fluid is provided for thermal conditioning of feed water in a water-steam cycle for operation of a steam turbine.
  • the feed water is thermally conditioned by means of heat transfer for preheating and/or also for evaporation. Further steps of the thermal conditioning, especially for superheating steam of the feed water, typically subsequently follow on from there.
  • Feed water is to be understood in this case both in the sense of condensate water which results in a coupled gas and steam power plant process, and also in the conventional sense of feed water which, for example, is provided for supplying an external steam process in an external steam power plant, for example.
  • the extraction of the heat exchanger fluid and/or of the thermal store fluid from the thermal store is carried out, wherein the extracted heat exchanger fluid and/or the thermal store fluid is provided for conditioning the intake air of the gas turbine during a normal power generating operation.
  • Such conditioning is typically carried out by means of an intake-air conditioner which is arranged in the induction region of the compressor stage.
  • the extraction of the heat exchanger fluid and/or of the thermal store fluid from the thermal store is carried out, wherein the extracted heat exchanger fluid and/or the thermal store fluid is introduced into a district heating network.
  • provision can be made for the inclusion of at least one post-heating stage which interacts with the gas flow downstream with regard to the gas turbine and upstream with regard to the first heat exchanger so that additional thermal energy can be supplied to the gas flow.
  • the temperature level of the gas flow can therefore be raised by additional thermal energy being made available to the gas flow from the post-heating stage. Consequently, a higher temperature level, and therefore a larger heat quantity, is available in the first heat exchanger and can be transferred to the heat exchanger fluid. Therefore, all further applications, which need to be supplied with thermally conditioned heat exchanger fluid, can be operated with a higher energy content or a higher heat quantity. This can especially have an advantageous effect upon the efficiency of these applications.
  • the post-heating stage provides thermal energy by means of a combustion process, which combustion process is especially a combustion process which is supplied with natural gas.
  • the natural gas can especially preferably be extracted from the fuel reservoir which also serves for supplying the gas turbine with fuel.
  • Natural gas moreover, in comparison to crude oil, for example, is a relatively environmentally more friendly energy source which can be combusted with higher efficiency and smaller residues. Accordingly, the present embodiment proves to be particularly environmentally suitable.
  • additional provision of a fuel is not necessary.
  • the heat transfer in the first heat exchanger is of sufficient magnitude to thermally convert the heat exchanger fluid into steam or into a superheated and pressurized fluid, wherein the heat exchanger fluid can preferably be stored under pressure in the thermal store.
  • the heat exchanger fluid is especially water and is stored in superheated form. This water can subsequently be fed to a steam process for use in a steam power plant.
  • the thermal store fluid can also fulfill this task instead of the heat exchanger fluid.
  • the heat exchanger fluid is water.
  • This can be contained in a steam circuit, for example.
  • a steam circuit is especially suitable for electric power generation, for example by means of a steam turbine. Consequently, the thermal energy contained in the heat exchanger fluid can be available to an efficient power generation process which in particular can also feed power, which is generated with a time delay, to the public electricity network.
  • the thermal store fluid is also suitable for this instead of the heat exchanger fluid.
  • the heat exchanger fluid and/or the thermal store fluid can be fed to an intake-air conditioner which is designed for preheating the intake air which is inducted into the compressor stage by means of the gas turbine during normal power generating operation.
  • an intake-air conditioner which is designed for preheating the intake air which is inducted into the compressor stage by means of the gas turbine during normal power generating operation.
  • the heat exchanger fluid and/or the thermal store fluid can be fed to a third heat exchanger which is designed for preheating feed water in the steam process for operating a steam turbine. Accordingly, the thermal energy content of the feed water can be increased in a suitable manner, as a result of which the subsequent power generation process can be carried out more efficiently by means of a steam turbine.
  • the heat exchanger fluid and/or the thermal store fluid are, or is, in thermal and/or fluid communication with a district heating network.
  • FIG. 1 shows a first embodiment of the gas power plant according to the invention in a schematic view
  • FIG. 2 shows a second embodiment of the gas power plant according to the invention in a schematic view
  • FIG. 3 shows a third embodiment of the gas power plant according to the invention also in a schematic view
  • FIG. 4 shows a flow diagram for describing an embodiment of the method according to the invention.
  • FIG. 1 shows a first embodiment of the gas power plant 1 according to the invention in a schematic view.
  • the gas power plant 1 comprises a gas turbine 10 which has a compressor stage 11 , a combustion chamber stage 12 and a turbine stage 13 .
  • the gas turbine 10 is connected to a generator 14 via a shaft 15 .
  • the generator 14 is connected to a public electricity network 17 and is suitable according to the invention for also being driven as a motor that consumes electrical energy from the public electricity network 17 .
  • the gas turbine 10 can be operated in a normal power generating mode that delivers electrical energy to the public electricity network 17 as well as in a mode which consumes electrical energy from the public electricity network 17 as the generator 14 acts as the motor to drive the shaft 15 for providing thermal heat.
  • the generator 14 is operated as a motor, wherein intake air is inducted into the compressor stage 11 , forming a gas flow 16 which passes through the combustion chamber stage 12 but without being mixed with a fuel in a quantity as would be added to the gas flow 16 during normal operation. In particular, no fuel is added to the gas flow 16 .
  • the gas flow 16 on account of the compression in the compressor stage 11 , increases in heat content as a result of fluid-dynamic compression. The gas flow 16 furthermore enters the turbine stage 13 and passes through this. In the process, the gas flow 16 can release energy to the turbine but to a considerably lesser extent than as would be the case in a normal power generating mode.
  • the gas flow 16 scarcely changes its temperature level as a result of the energy loss to the turbine.
  • the gas flow 16 flows into a gas routing device 20 and is directed in a suitable manner to a first heat exchanger 30 at which the thermal energy from the gas flow 16 is released to a heat exchanger fluid (not shown in the present case).
  • the post-heating stage 40 can be supplied with natural gas as fuel by means of a natural gas feed line 45 , wherein as a result of a combustion process the combustion heat can be released to the gas flow 16 by means of the post-heating stage 40 . Consequently, it can be ensured that the first heat exchanger 30 is supplied with sufficient thermal energy.
  • the first heat exchanger 30 is in thermal functional communication with a circuit of the heat exchanger fluid.
  • the heat exchanger fluid can be extracted according to the embodiment from the circuit as steam via a steam line 32 in order to be available to further steam-engineering applications.
  • thermal store fluid (not shown in the present case) which, for example, can be temporarily stored in a thermal store 50 .
  • the thermal store fluid absorbs thermal energy in the second heat exchanger 35 so as to be stored in the thermal store 50 for later use.
  • the heat exchanger fluid can also be stored in the thermal store 50 for later use.
  • the thermal store fluid can, for example, be extracted again from the thermal store 50 via an extraction line 56 .
  • the thermal store fluid can, for example, be extracted for supplying a district heating line.
  • extraction of thermal energy can also be achieved by means of a third heat exchanger 60 .
  • the heat exchanger 60 can be adapted in this case for pre-specified thermal applications. Such applications can, for example, be the preheating of feed water or the preheating of process fluid as well as the preheating of process gases.
  • FIG. 2 shows a further embodiment of the gas power plant 1 according to the invention, which differs from the embodiment shown in FIG. 1 only to the effect that the gas routing device 20 has a steam generator unit 71 .
  • the steam generator unit 71 is preferably provided in the gas routing device 20 between the post-heating stage 40 and the gas turbine 10 .
  • the steam generator unit 71 is used for steam generation during the normal power generating operation of the gas turbine 10 , wherein the steam generated in this way can be fed to a steam turbine 70 for driving it.
  • An improvement according to the embodiment is achieved by providing thermal energy via the third heat exchanger 60 which extracts from the thermal store 50 the energy of the thermal store fluid which is stored therein.
  • heat, or preheated fluid water, for example
  • water water, for example
  • the steam generator unit 71 in this case can have further preheating stages or even just one steam generator or superheater.
  • the preheating of the fluid (water, for example) which is fed to the steam generator unit 71 proves to be particularly advantageous when the gas turbine 10 is changed over from an idling state to an operating stage. If the fluid which is provided in the steam generator unit 71 is specifically already at a higher temperature level at the point in time of start-up of the gas turbine, the point of steam generation is initiated at a relatively earlier point in time. Accordingly, the steam turbine 70 can also be used for power generation at a relatively earlier point in time. Consequently, the start-up times for operation of the steam turbine 70 can therefore be reduced.
  • the transfer of thermal energy to the fluid which is fed to the steam generator unit 71 can also be carried out by means of the second heat exchanger 35 .
  • FIG. 3 shows a further embodiment of the gas power plant 1 according to the invention which differs from the embodiment shown in FIG. 1 only to the effect that thermal energy can be extracted from the thermal store 50 by means of the third heat exchanger 60 , wherein this energy is fed to an intake-air conditioner 62 which is designed for preheating the intake air which is inducted into the compressor stage 11 during a normal power generating operation of the gas turbine 10 .
  • FIG. 4 shows a flow diagram for describing an embodiment of the method according to the invention.
  • the generator 10 in a first step the generator 10 is operated as a motor in order to form a gas flow 16 which has an increased temperature level in comparison to the ambient temperature.
  • the gas flow 16 which discharges from the turbine stage 13 and has an increased thermal energy level, is diverted, i.e. is guided in a desired direction.
  • the gas flow 16 is then fed to a first heat exchanger 30 for transferring at least some of the thermal energy to a heat exchanger fluid.
  • This can then be temporarily stored according to the embodiment in a thermal store 50 for later consumption.
  • the thermal energy can also be transferred in a second heat exchanger 35 to a thermal store fluid, not additionally shown, which can also be provided for temporary storage in a thermal store 50 .

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Power Engineering (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Control Of Eletrric Generators (AREA)
US14/379,439 2012-02-20 2013-02-01 Gas power plant Expired - Fee Related US9341114B2 (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102012202575 2012-02-20
DE102012202575A DE102012202575A1 (de) 2012-02-20 2012-02-20 Gaskraftwerk
DE102012202575.8 2012-02-20
PCT/EP2013/052018 WO2013124135A1 (fr) 2012-02-20 2013-02-01 Centrale à gaz

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US20150035277A1 US20150035277A1 (en) 2015-02-05
US9341114B2 true US9341114B2 (en) 2016-05-17

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US (1) US9341114B2 (fr)
EP (1) EP2802757B1 (fr)
JP (1) JP5998230B2 (fr)
KR (1) KR101514621B1 (fr)
CN (1) CN104136742B (fr)
DE (1) DE102012202575A1 (fr)
DK (1) DK2802757T3 (fr)
WO (1) WO2013124135A1 (fr)

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KR102163053B1 (ko) * 2015-09-07 2020-10-08 삼성전기주식회사 압전 진동편 및 압전 진동자
KR102506171B1 (ko) * 2018-05-22 2023-03-07 지멘스 에너지 글로벌 게엠베하 운트 코. 카게 팽창기를 갖는 확장 가스 터빈 프로세스
US11512635B2 (en) * 2019-09-26 2022-11-29 Halliburton Energy Services, Inc. Gas turbine waste heat utilization
JP2021088977A (ja) * 2019-12-05 2021-06-10 株式会社Ihi 排熱蓄熱システム
DE102020201068A1 (de) 2020-01-29 2021-07-29 Siemens Aktiengesellschaft Anlage mit thermischem Energiespeicher, Verfahren zum Betreiben und Verfahren zur Modifikation

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JP5998230B2 (ja) 2016-09-28
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JP2015512009A (ja) 2015-04-23
KR20140116977A (ko) 2014-10-06
EP2802757B1 (fr) 2018-05-30
US20150035277A1 (en) 2015-02-05
EP2802757A1 (fr) 2014-11-19
KR101514621B1 (ko) 2015-04-22

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